EP0775080A1 - Systeme de levage de charges - Google Patents

Systeme de levage de charges

Info

Publication number
EP0775080A1
EP0775080A1 EP96917428A EP96917428A EP0775080A1 EP 0775080 A1 EP0775080 A1 EP 0775080A1 EP 96917428 A EP96917428 A EP 96917428A EP 96917428 A EP96917428 A EP 96917428A EP 0775080 A1 EP0775080 A1 EP 0775080A1
Authority
EP
European Patent Office
Prior art keywords
load
cable
cables
lifting system
drum
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96917428A
Other languages
German (de)
English (en)
Other versions
EP0775080B1 (fr
Inventor
Hans Tax
Dieter Bauer
Klaus HÖSLER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
TAX ImbH
Original Assignee
TAX ImbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by TAX ImbH filed Critical TAX ImbH
Publication of EP0775080A1 publication Critical patent/EP0775080A1/fr
Application granted granted Critical
Publication of EP0775080B1 publication Critical patent/EP0775080B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/04—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack
    • B66C13/08—Auxiliary devices for controlling movements of suspended loads, or preventing cable slack for depositing loads in desired attitudes or positions
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/48—Control devices automatic
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D2700/00—Capstans, winches or hoists
    • B66D2700/02—Hoists or accessories for hoists
    • B66D2700/023—Hoists

Definitions

  • the present invention relates to a load lifting system of the type mentioned in the preamble of claim 1.
  • the term “prisms” includes similar bodies such as cuboids, cubes or truncated pyramids.
  • the term “cable pull” includes simple load cables as well as pulley blocks with a lower, loose roller arrangement.
  • Load lifting systems of the generic type are used in particular for lifting and handling large containers.
  • the crane scaffold is generally a rail-bound or free-moving container pallet truck with a trolley which carries the load lifting system.
  • the movement of the container lift truck enables large-scale transport of the container between individual stacking places.
  • the rough positioning of the container at the stacking station in the two horizontal axis directions is again carried out by the movement of the container lift truck and possibly by the movement of a trolley; the general
  • the lifting and lowering movement takes place via an actuation of the cable drums; in general, several or all of the cables of a load lifting system are generally guided on a common cable drum.
  • the movement possibilities described generally do not allow the load to be positioned and aligned with the accuracy required in modern container handling operations.
  • the permissible positional deviation, for example of two large containers stacked on top of each other, is a maximum of 10 mm. This results in the necessity to create means for shifting and rotating the load lifting system in the horizontal plane by small amounts.
  • FIG. 1 This shows schematically an approximately cuboid container C with a main transverse axis X, a main longitudinal axis Y and a vertical axis Z. Shifts in the direction of the X and Y axes are rotations about the X axis, the Y and X movements -Axis or the Z-axis are referred to as pitching, rolling or yawing movements. These designations are also used in the following.
  • Load lifting systems of the type mentioned in the preamble of claim 1 are already known, in which a so-called head block (head block) is arranged between the actual cable pull arrangement and a holding frame that can be coupled to the container, said head block consisting of two mutually movable and in the sense of the above described micro-movements cash frame or the like. With its storage and adjustment devices, such a head block represents a technically extremely complex and heavy component, which makes the load lifting system considerably more expensive.
  • each is defined by two load levels
  • Each corner area of the fictitious prism is assigned a pair of cable pulls, each of which comprises a cable pull from one of the two load planes forming the corner.
  • additional adjustment means are provided in order to adjust the cable pulls of at least individual cable pull pairs in the same direction and in a coordinated manner. These additional adjustment means make it possible to raise or lower individual corners or edges of the fictitious prism and in this way tilt the load lifting system around one or both of the horizontal axes which are perpendicular to one another.
  • At least two pairs of cable pulls adjacent in the direction of a main longitudinal axis and / or two cable pull pairs adjacent in the direction of a main transverse axis of the prism are equipped with the additional adjusting means.
  • the simultaneous and same-directional adjustment of two adjacent cable pull pairs immediately results in a tilting movement about one of these two axes.
  • the term "to be adjusted in a coordinated manner" means that in general, in the case of the cable pulls involved in a tilting movement, any differences in their distance from the tilting axis must be taken into account.
  • cable force compensation devices are provided between at least individual cable pulls of the load lifting system. With such cable force compensation devices it can be achieved that all cables connected to such a device carry the same loads. This makes it possible, for example, to compensate for uneven changes in length of the ropes, uneven rope reel diameters, etc.
  • Such cable force compensation devices are provided in particular between two cables of a pair of cables.
  • the adjustment mechanisms for an opposite adjustment of the rope trains of a load level are released in each case. This measure makes it possible that, for example, if external horizontal forces act on the load due to high driving accelerations and shift it, the adjustment mechanisms affected by this shift can follow the shifting movement, in order in this way to slacken individuals Prevent sections of rope.
  • an adjustment mechanism for the opposite adjustment of the cables of a load level it is provided that the free ends of the two cables of a load level are coupled to one another and that an adjustment drive which is adjustable in two directions acts on the coupled cable.
  • a hydraulic actuating cylinder, an electric threaded spindle drive or the like can be considered as the adjusting drive. If the rope formed by connecting the two free ends is adjusted in one direction, one end of the rope is adjusted in the sense of shortening the assigned cable, the other end of the rope in the sense of an extension of the associated cable, so that the desired opposite adjustment of the two cables with a single actuator.
  • the free ends of the two cable pulls of a load plane are each articulated on a connecting link arrangement, and that an adjusting drive which is adjustable in two directions acts on the connecting link arrangement.
  • a connecting link arrangement with the associated adjusting drive and, if appropriate, further components described below can be preassembled as a structural unit, so that only the free cable ends need to be connected to this arrangement when the load lifting system is installed.
  • Such a connecting link arrangement is explained in more detail using an exemplary embodiment.
  • the adjusting drive can be detachable from the cable arrangement.
  • the adjusting drive remains firmly connected to the cable arrangement and can even be switched without power.
  • the two cylinder chambers on both sides of the actuating piston are short-circuited for this purpose.
  • the means for adjusting individual pairs of cable pulls in the same direction can in principle act on the free ends or on the drum ends of the cable pulls.
  • they engage the drum ends and are formed by adjustable length compensation rollers over which the assigned cable ends are guided.
  • the length compensation rollers By moving or pivoting the length compensation rollers, the cable path is shortened or lengthened in a manner known per se, and the associated cable pull is thus lengthened or shortened.
  • the two pairs of cable pulls arranged on one side of this main axis can be adjusted in the same direction, as was mentioned earlier.
  • the cable force compensation devices each comprise a single-acting hydraulic cylinder arranged in the course of the cable or in series with a cable of the associated cables, the cylinder chambers under load of the hydraulic cylinders of a cable force compensation device being connected to one another via a compensation line.
  • the pressures in the hydraulic cylinders of a cable force compensation device compensate each other via the compensation lines until the same pressure prevails in all the hydraulic cylinders and thus the same tensile force in all the cables.
  • the adjustment mechanisms for the opposite adjustment of the cable pulls of a load level are assigned shock absorber means which dampens the movement of the adjustment mechanism induced, for example, by accelerations, especially when the adjustment drive is enabled.
  • a particularly advantageous arrangement for the function of the load lifting device is obtained when the loose rollers of the cable pulls of a pair of cable pulls engage essentially at the same load point, and when all cable pulls are constructed essentially geometrically the same.
  • the cable pulls of a pair of cable pulls always carry out the same length changes in all positioning movements, which leads to a considerable simplification, in particular of the additional adjustment means for the adjustment of the cable pull pairs in the same direction.
  • the cables are preferably simple pulleys with a loose pulley, the end of the drum being essentially vertical and the free end being at an acute angle to the vertical.
  • FIG. 1 schematically shows a container with the different directions of movement
  • FIG. 2 schematically shows the cable guide in a load lifting system with load harnesses arranged in four load levels, each consisting of two pulleys;
  • FIG. 3 shows a load lifting system in a front view
  • FIG. 6 shows a view approximately according to FIG. 3 in an enlarged partial illustration
  • FIG. 7 shows a view approximately according to FIG. 4 in an enlarged partial illustration
  • FIG. 8 is a view approximately according to FIG. 5 in an enlarged representation
  • FIG. 10 schematically shows another embodiment of a load lifting system.
  • Fig. 1 shows schematically the example of a container C, the possible micro-movements that are required for precise positioning and orientation of a load. These movements include displacements in the X direction and Y direction as well as rotations about the X axis, the Y axis and the Z axis.
  • a load lifting system of the generic type with four load levels generally comprises a pulley arrangement 2 suspended from a crane frame (not shown), a holding frame 4 (spreader) hanging from this pulley arrangement adaptable to different dimensions of the container C and provided with coupling means 6 for coupling with the container C.
  • a load lifting system of the generic type with four load levels generally comprises a pulley arrangement 2 suspended from a crane frame (not shown), a holding frame 4 (spreader) hanging from this pulley arrangement adaptable to different dimensions of the container C and provided with coupling means 6 for coupling with the container C.
  • 3 and 4 show the pulley arrangement 2 in a lower and an upper position.
  • FIG. 2 schematically and generally shows a typical cable guide for a load lifting system of the generic type.
  • two pulleys are arranged, which are denoted by Fl to F8 .
  • the pulley blocks are designed as simple pulley blocks, each with a lower, loose roller R, from which the drum end T of a traction cable S is guided vertically upwards and optionally after deflections onto a cable drum, not shown, while the other, free end E is guided obliquely upwards to a fastening point P of the crane scaffold, not shown.
  • the angles o between the drum end and the free end are preferably the same for all pulley blocks.
  • Such a pendulum-free load lifting system is known in principle and is also referred to as a "rope tower".
  • 3 to 5 show schematically in three different views a load lifting system with a cable guide essentially corresponding to FIG. 2. The same designations as in FIG. 2 are therefore used here.
  • the elements of the eight pulley blocks are each identified by a reference symbol and an index number from 1 to 8.
  • a similar adjustment mechanism H3, H4, K3, 4 is assigned to the cylinder trains of the load level L2 shown in FIG. 4.
  • the drum ends T4 and T5 (the latter is covered in FIG. 4) are in the corner defined by the load planes L2 / L3 via upper deflection rollers 04 and 05 and via further deflection rollers Q4 and Q5 led on the Seil ⁇ drum 8.
  • the additional deflection rollers Q4 and Q5 can be adjusted in accordance with arrow 10, so that the associated pulleys F4 and F5 can be shortened or lengthened as desired.
  • the drum ends T6 and T7 of the block and tackle F6 and F7 in the corner defined by the load levels L3 / L4 are also Via upper deflection rollers 06 or 07 and via additional deflection rollers Q6 or Q7 to the cable drum 8 (see FIG. 5).
  • the upper deflection rollers 04 and 05 or 06 and 07 can each be designed as coaxial double rollers, as shown in FIG. 5.
  • the additional deflection rollers Q6 and Q7 are also adjustable in the direction of arrow 10.
  • the pulleys F4, F5, F6, F7 are adjusted in the same direction, so that the container C performs a tilting movement about the X axis.
  • the drum ends T8 and T1 to T3 in the corners defined by the load planes L4 / L1 and L1 / L2 are also guided via upper deflection rollers 08 and 01 to 03 and from there directly to the cable drum 8 (see also FIG. 5).
  • the drum ends T2 and T3 of the pair of pulley blocks F2, F3 could also be guided over additional, adjustable deflection pulleys in order to adjust this pair of pulley blocks in the same direction as the pair of pulley blocks F4, F5 .
  • another path, described below, is followed for the tilting about the Y axis.
  • a certain winding section of the cable drum 8 is assigned to each drum end of a rope, the inlet angle of the running drum end changing in a known manner during the winding or unwinding process.
  • FIG. 9 shows an exemplary embodiment of an adjustment mechanism for the opposite adjustment of two cable pulls of a load level, specifically for the load level L1 from FIG. 2.
  • the adjustment mechanism is also assigned an actuator, a damping device and a cable force compensation device as explained below.
  • the free ends E1 and E2 are guided on segment levers H1 and H2, respectively, pivotably arranged in the load plane and fastened to them.
  • Angular levers W1 and W2 are arranged coaxially to the segment levers H1 and H2, respectively, which are pivotable relative to the segment levers.
  • the angle levers W1 and W2 are connected to the associated segment levers H1 and H2, respectively, via a cable force compensation cylinder ZI and Z2.
  • the free ends of the angle levers W1 and W2 are connected to one another via a coupling rod Kl, 2. Since the free ends El and E2 are always tension-loaded, the cable force compensation cylinders ZI and Z2 and the coupling rod Kl, 2 are always tension-loaded; the coupling rod could therefore also be replaced by a rope.
  • the respective cable force compensation cylinder can be omitted, the segment lever and the associated angle lever being integrated into a rigid component.
  • the hydraulic actuator 12 which can be actuated in two directions, is provided. This is firmly connected to the coupling rod Kl, 2 via a tab 14. The actuator 12 can be short-circuited via a short-circuit line 16 and thus switched off.
  • the function of the load lifting system is as follows:
  • the cable drum 8 common to all the cable pulls is actuated, so that all cable pulls are adjusted uniformly.
  • FIGS. 3 and 4 at which the end walls of the container C are essentially parallel to the load planes L1 and L3, the side walls are essentially parallel to the load planes L2 and L4.
  • the adjustment mechanisms of the load levels Ll and L3 are adjusted in the same direction.
  • a tilting of the container C is prevented by the load harnesses of the load levels L2 and L4 which remain unchanged.
  • a shift in the Y direction is carried out by actuating the adjustment mechanisms of the load levels L2 and L4 in the same direction, the container being prevented from tipping about the X axis by the load harnesses of the load levels Ll and L3 remaining unchanged.
  • the adjustment mechanisms of the load levels L1 and L3 on the one hand and of the load levels L2 and L4 on the other hand are each adjusted in opposite directions. It may also suffice to adjust only the adjustment mechanisms of the load levels L1 and L3 in opposite directions and to release the adjustment mechanisms of the load levels L2 and L4.
  • a tilting movement of the container C about the X-axis is carried out by adjusting the cables F4, F5 and F6, F7 in the same direction by adjusting the assigned additional deflection rollers Q4, Q5 and Q6, Q7 in the same direction.
  • the possibility of switching the adjustment mechanisms or their adjustment drives 12 into a power-free state fulfills another important task. If, for example, the load is accelerated so strongly in the direction of a horizontal axis, for example the X axis, as a result of high driving accelerations that individual ropes of the load planes L1 and L3 lying parallel to this axis threaten to become slack, the adjustment mechanisms become released these load levels, so that the load harness can adapt to the horizontal deflection resulting from the acceleration.
  • FIG. 10 shows a load lifting system in which the cable pulls in the four load levels are designed as simple cables.
  • the load levels are denoted by Ll to L4 and the ropes by Sll to S18.
  • a drum end of each of the ropes S11 to S18 is optionally guided via deflection rollers to an assigned rope drum 20 or 22.
  • the other, free ends of the ropes S11 and S18 are each guided to a fastening point on the holding frame 24 which can be coupled to the load, for example a container.
  • the two ropes of a load level form a load harness.
  • the same adjustment mechanism is assigned to the load level L3 or the ropes S15 and S16.
  • the free ends of the cables S17 and S18 of the load plane L4 are connected to one another and placed around a cable drum 28.
  • the cable drum 28 can be rotated by means of an adjusting drive 30, the cables S17 and S18 being adjusted in opposite directions.
  • the same adjustment arrangement is assigned to the load level L2 or to the cables S13 and S14.
  • this arrangement enables movements in the X direction by actuating the adjustment mechanisms in the load planes L1 and L3 in the same direction, movement in the Y direction by actuating the adjustment mechanisms in the load planes L2 and L4 in the same direction, and rotation about the vertical axis by actuating in opposite directions at least two adjusting mechanisms arranged in mutually parallel load planes.
  • Additional adjustment means for executing a rolling or pitching movement are not shown, but can be formed, as in the first exemplary embodiment, by adjustable length compensation rollers over which the drum ends of the cable pulls are guided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Load-Engaging Elements For Cranes (AREA)
  • Types And Forms Of Lifts (AREA)

Abstract

L'invention concerne un système de levage de charges avec plusieurs câbles coopérants, suspendus à un portique. Au moins deux câbles sont affectés, par exemple, à quatre plans de charge formant les côtés d'un parallélépipède rectangle fictif, les forces résultantes de ces câbles se trouvant dans le plan de charge associé et étant inclinées de façon symétrique à la verticale l'une par rapport à l'autre. Une première extrémité (extrémité côté tambour) de chaque câble passe un tambour à câble et l'autre extrémité du câble (extrémité libre) est amenée vers un point de fixation. Afin de positionner avec précision la charge suspendue au système de levage, par exemple un conteneur (C), dans le plan horizontal, il est prévu que les extrémités libres (E) des câbles (S) de chaque plan de charge (L) soient respectivement reliées à un de ces premiers mécanismes de réglage communs (H, K) qui réalisent un réglage identique et inverse de ces extrémités libres (E) et donc modifient la longueur des câbles d'une même valeur en sens inverse. Grâce à ce réglage les câbles du plan de charge associé sont déviés latéralement lorsqu'un basculement est empêché, par exemple par les câbles de longueur non modifiée des deux plans de charge qui leur sont perpendiculaires.
EP96917428A 1995-06-09 1996-05-24 Systeme de levage de charges Expired - Lifetime EP0775080B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19521066A DE19521066A1 (de) 1995-06-09 1995-06-09 Lasthebesystem
DE19521066 1995-06-09
PCT/EP1996/002252 WO1996041763A1 (fr) 1995-06-09 1996-05-24 Systeme de levage de charges

Publications (2)

Publication Number Publication Date
EP0775080A1 true EP0775080A1 (fr) 1997-05-28
EP0775080B1 EP0775080B1 (fr) 2000-03-08

Family

ID=7764008

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96917428A Expired - Lifetime EP0775080B1 (fr) 1995-06-09 1996-05-24 Systeme de levage de charges

Country Status (5)

Country Link
EP (1) EP0775080B1 (fr)
JP (1) JPH10507435A (fr)
KR (1) KR970704623A (fr)
DE (2) DE19521066A1 (fr)
WO (1) WO1996041763A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6441299B2 (en) 1998-12-07 2002-08-27 Bridgestone Corporation Covering member for solar battery
JP2009504945A (ja) * 2005-08-11 2009-02-05 フランツ プラッサ バーンバウマシーネン−インダストリーゲゼルシャフト エムベーハー 軌道を再敷設するための機械

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19918449C2 (de) * 1999-04-23 2001-09-13 Noell Stahl Und Maschb Gmbh Lasthebesystem zur Feinpositionierung und aktiven Schwingungsdämpfung
DE50002056D1 (de) * 1999-11-30 2003-06-12 Tms Produktionssysteme Gmbh & Laufkatzen-Seilhubwerk mit Pendeldämpfung
DE10132350B4 (de) * 2001-07-04 2005-11-10 Eisenmann Maschinenbau Gmbh & Co. Kg Hubvorrichtung
JP4303777B1 (ja) * 2008-11-26 2009-07-29 三井造船株式会社 クレーンのロープ掛け構造
JP5457060B2 (ja) * 2009-03-30 2014-04-02 三井造船株式会社 クレーンのロープ掛け構造
JP5394793B2 (ja) * 2009-03-30 2014-01-22 三井造船株式会社 クレーンのロープ掛け構造
JP5529438B2 (ja) * 2009-05-27 2014-06-25 三井造船株式会社 クレーンのロープ掛け構造
DE102009034121A1 (de) * 2009-07-20 2011-01-27 Thyssenkrupp Millservices & Systems Gmbh Hubwerk eines Krans
CN105565173A (zh) * 2015-12-31 2016-05-11 上海市机械施工集团有限公司 超重巨柱双机抬吊安全扁担框吊装装置及其使用方法

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US3081884A (en) * 1961-06-09 1963-03-19 Manning Maxwell & Moore Inc Crane with anti-sway mechanism
US3828940A (en) * 1971-09-03 1974-08-13 Fruehauf Corp Spreader list, trim and skew adjustment means
JPS5882986A (ja) * 1981-11-11 1983-05-18 株式会社日立製作所 つり具の制御装置
JPS5982290A (ja) * 1982-11-01 1984-05-12 株式会社日立製作所 クレ−ンの吊具傾転装置
DD221444A1 (de) * 1984-02-21 1985-04-24 Kranbau Wittenberg Takraf Veb Vorrichtung zum schraegstellen von lastaufnahmemitteln
FR2643353B1 (fr) * 1989-02-17 1991-06-14 Caillard Dispositif pour eviter le balancement d'une charge sous un bati de support, notamment un portique
DD291064A5 (de) * 1989-12-28 1991-06-20 Veb Schachtbau Nordhausen,De Einrichtung fuer den ausgleich von seilablaufdifferenzen bei mehrwindenhubwerken
DE4142778C2 (de) * 1991-12-23 1997-11-20 Man Takraf Foerdertechnik Gmbh Vorrichtung zur Spreaderpositionierung bei Containerkranen

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6441299B2 (en) 1998-12-07 2002-08-27 Bridgestone Corporation Covering member for solar battery
JP2009504945A (ja) * 2005-08-11 2009-02-05 フランツ プラッサ バーンバウマシーネン−インダストリーゲゼルシャフト エムベーハー 軌道を再敷設するための機械

Also Published As

Publication number Publication date
WO1996041763A1 (fr) 1996-12-27
EP0775080B1 (fr) 2000-03-08
JPH10507435A (ja) 1998-07-21
DE19521066A1 (de) 1996-12-12
DE59604595D1 (de) 2000-04-13
KR970704623A (ko) 1997-09-06

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